Positive displacement pump



Nov. 21, 1967 Filed Feb. 9, 1966 E. F. WRIGHT 3,353,490

POSITIVE DISPLACEMENT PUMP 2 Sheets-Sheet 1 DUPLEX STEAM PUMP PiSTON VELOCITY t I 0 3 so m a B O 0 3'0 60 9o I I30 2IO 24-0 270 300 330 360 EQUIVALENT CRANK ANGLE DEGREES (0R CYCLE TIME) FIG. 3 Fl 6. 4-

PLUNGER VELOCITY K(lcos 2) FOR sMov-m new DUPLEX PU P PLUNGER DISPLACEMENT =I (u-sm2o.) OPTIMUM VALVE szA-rme AND OPENING 0 so E 5 U 0 g, 40 5 20 9 5 o 20 40 so an no 120 no see no zoo no 240 260 no 300 37.0 340 360 PLUNGER DISPLACEMENT"% EQUIVALENT cRAuK ANGLE DEGREES (on TIME FOR CYCLE) FIG.5

0 Z0 40 60 8 I00 I20 I40 I60 I60 200 220 240 25 2% 300 320340 360 EQUIVALENT CRANK ANGLE-DEGREE5(OR TIME FQR CYCLE) I N VENTOR.

Nov. 21, 1967 E. F. WRIGHT POSITIVE DISPLACEMENT PUMP T R H N @1 mm m Rw 2 2 Wm H W- l l l l l I I l I II F w w O QM U Y L B E Filed Feb. 9, 1966 United States Patent 3,353,490 PQSITEVE DISPLACEMENT PUMP Elliott F. Wright, Warren Township, Somerset County, NJL, assignor to Worthington Corporation, Harrison, N..I., a corporation of Delaware Filed Feb. H66, Ser. No. 526,105 8 Qlafms. (Cl. 103-4h) ABSTRAQT 0F THE DESCLOSURE A positive displacement pump having power cylinders driven by either a constant capacity or variable capacity driver. Said pump having a valve arrangement comprising a pair of speed control valves and a pair of reversing valves for controlling the passage of power fluid to and from the power cylinders of the pump. Primary control of each speed control valve is affected by interconnecting the speed control valve to the piston it controls, and secondary control of each speed control valve is taken from the piston on the opposite side. In this fashion the speed control valves throttle and cut-off power fluid as desired, producing the ideal displacement and velocity pattern for the pump pistons.

This invention relates to reciprocating type displacement pumps and more particularly to a valve and speed control arrangement which facilitates obtaining a constant and non-pulsating rate of flow of fluid into and out of the pump and optimum piston velocity throughout the working cycle or stroke of the pump.

Prior art concepts lack effective means for reducing the cyclical flow variations and resulting pressure fluctuations inherent in pumps using a relatively small number of plungers or the like driven by a crank and connecting rod or their equivalent.

These pressure fluctuations are particularly harmful to the valving of the pump. Specifically one of the results is slamming of the valves in opening and closing and accordingly very slow crank speeds are necessary.

There are also other reasons necessitating slow rotative speeds with conventional pumps. Another of these is due to the large variations in rate of flow of the combined cylinders. With any single reciprocating plunger the rate of flow is zero at each end of the stroke. To even out the combined flow, multicylinder arrangements are used and in general the more cylinders used, the smoother the flow or the smaller the variations in flow.

Another important speed limitation is caused by the need for keeping the piston accelerations down to values low enough to allow'the liquid from the suction line to flow to the piston on the suction stroke. Where only atmospheric pressure is available in the suction line to pro vide acceleration of the liquid coming therefrom, which must work against the suction lift and other elements slowing it down, very little pressure remains for accelerating the liquid to follow the piston. As a consequence, voids in the cylinder result and destructive impacts caused by cavitation occur. To highlight some of the above proble'ms, FIGURE 1 is submitted and shows, in the traditional duplex double acting steam pump, the very sharp acceleration of the pistons at each end of the stroke and a practically constant velocity of one piston throughout most of the stroke while the other piston is idle. As was mentioned above, this action is unfavorable to operation of the pump valves, and the rapid acceleration of the pistons causes pressure fluctuations and surges at each reversal.

Applicant in United States Patent 3,179,056 devised an arrangement, for solving many of the above drawbacks, which included a valve member driven by the opice posite side plunger to stop and start the first piston with the other piston moving at its maximum velocity at the critical moment of reversal of the first piston.

However, in manufacturing the valve arrangement and particularly the shape of port contemplated in Patent 3,179,056, it was found extremely diflicult to produce. This in effect reduces the commercial potential of this prior arrangement.

To overcome this problem, applicant contemplates the incorporation, in a positive displacement pump driven by either a constant capacity or variable capacity driver, of a valve arrangement comprising a pair of speed control valves and a pair of reversing valves for controlling the passage of power fluid to and from the power cylinder. Primary control of the speed control valve is effected by interconnection of same to the piston it controls and secondary control of the speed control valve is taken from the opposite side piston. In this fashion the speed control valves throttle and cut off power fluid as desired, producing the ideal displacement and velocity pattern throughout the higher speed portion of the operating range of the pump.

Accordingly, it is an object of this invention to provide an improved positive displacement pump capable of being associated with either a constant or variable capacity prime mover.

It is a further object of this invention to provide an improved positive displacement pump capable of being associated with either a constant or variable capacity prime mover which facilitates obtaining a constant and non-pulsating rate of flow of fluid into and out of the pump and optimum piston velocity throughout the working cycle or stroke of the pump.

It is another object of the present invention to provide an improved general service type pump designed to obtain the ideal piston velocity and displacement pattern described by V=K(1cos 2A) and D=K( as shown in FIGURES 5 and 6 of the drawings.

It is a further object of this invention to provide a valve arrangement for a positive displacement reciprocating pump which overcomes the above mentioned drawbacks.

ther objects and advantages of the invention including the basic design and the nature of the improvements thereon will appear from the following descriptions taken in conjunction with the following drawings, in which:

FIGURE 1 is a diagrammatic view showing a curve representing a duplex direct acting steam pump piston velocity.

FIGURE 2 is a diagrammatic view of a positive displacement fluid driven pump showing the present invention.

FIGURE 3 is an enlarged fragmentary view of one form of reversing valve.

FIGURE 4 is an enlarged fragmentary view of one of the speed control valves shown in FIGURE 2.

FIGURE 5 is a diagrammatic view showing a curve representing the ideal piston velocity corresponding to FIGURE 6 is a diagrammatic view showing a curve representing the piston displacement corresponding to reference characters identify the same parts in the several views. Primes are used to distinguish the power pump unit at the bottom of FIGURE 2 from the power pump unit at the top.

Referring to the exemplary embodiment of the invention inFIGURE 2 there is shown a positive displace-ment pump comprising plural cylinders and 15, each housing plungers or pistons 16 and 16' which are reciprocated in the cylinders to pump fluid through the delivery ports 17. An intake supply is provided to the cylinders from a source through the intake ports 18. Suitable valves not shown are disposed in the valve housing 19 to regulate the inflow and outflow of the fluid to and from the cylinders 15 and 15. A driving means 20, which is preferably a well known variable capacity pump or a constant capacity unit called a supply means herein is connected to the power means or power cylinders 21 and 21; through a control means or control valve chest designated 22. Each pair of plungers 16 and 16' are disposed coaxially and on opposite sides of the power cylinder 22 and connected respectively to a piston 23 and 23' through shafts designated 25 and 25.

Power fluid is supplied to the driving means from reservoir 26 and is passed through line 27 to the control means 22.

The control means or control valve chest 22 serves as a housing for a plurality of speed control valves 34 and 34- and a plurality of reversing valves 28 and 28'; the pair of valves 28 and 34 selectively control passage of fluid through either conduit or line 29 or 30 to chamber 31 or 32 of power cylinder 21 to urge the power cylinder to move the plunger or piston 16 in the desired direction. Similarly valves 28' and 34' selectively control passage of fiuid through either conduit or line 29' or 30' to chamber 31 or 32' to power cylinder 21 to urge the power cylinder to move the plunger 16' in the desired direction. The specific function of the valves mentioned above will be described in detail hereinafter.

In order to overcome the drawbacks of prior type units as mentioned above, reversing valves 28 and 28' are respectively tied to plungers 16' and 16 and primary control of speed control valve 34 is through action of plunger 16 whereas primary control of speed control valve 34 is through action of plunger 16. An arrangement is also provided for accomplishing secondary control of valves 34 and 34' respectively through action of plungers 16 and 16.

More particularly, valve 28 is connected to rod by rod 36 and lever 37 which moves about fixed pivot point A. Valve 34 is connected to rod 25 by rod 42, lever 45, link 47 and lever 43. In this fashion primary control of valve 34 is accomplished by piston 23. Similarly, valve 28' is connected to rod 25 thru rod 40 and lever 41. Valve 34' is connected to rod 25 by rod 38, lever 46, link 48 and lever 39 so that primary control of this valve 34' is accomplished thru action of piston 23.

An arrangement of levers and cranks interconnects the levers 39 and 43 so that secondary control is provided for respectively by action of plungers 16 and 16. Specifically lever 45, link 49, crank 51, link 53 and crank 52 join valve 34 to rod 25'. Lever 46, link 50, cranks 60 and 61 and link 54 join valve 34 to rod 25. This dual lever and crank arrangement permits the secondary valve control mentioned above.

With the above arrangement the power cylinder drives its own speed control valve, continuing to the point of cut-01f of working fluid supply at the end of the stroke. The top or left hand piston 23 is at mid-stroke with its reversing valve 28 wide open at the end of its travel and its speed control valve 34 wide open at its center position. Fluid is passing from supply means 20 thru speed control valve 34 to port 35 to line 29 and returning via line to port 33 to line 44 to the reservoir 26. Piston 23' has reached the end of its stroke and lever 39, link 48 and valve rod 38 have pulled the speed control valve 34' to the cut-off position. At the same time, the motion of 4 piston 23 thru rod 25, lever 41 and rod 40 has pushed the reversing valve 2 to mid position.

The arrangement interconnecting the valves, referred to as a feedback or compensating linkage, now takes over to reverse the speed control valve 34 to start a supply of working fluid to start the return of piston 23'; reversing valve 28' is by then suitably positioned beyond center by the motion of piston 23. With primary control link 48 momentarily stationary; lever 43, thru its crank 61, link 54, crank 60, link 50 and compensating lever 46, moves valve 34 sufliciently to the left to start movement of piston 23.

During the first half of the piston stroke the compensating linkage adds to the control valve motion supplied primarily by lever 39 (and lever 43 for the opposite side). During the second half of any stroke the opposite side has reversed so that the compensating linkage detracts from the motion in preparation for reopening the valve after cut-off. This has the advantage at any point in the stroke of providing a slightly larger opening thru the speed control valve while the piston is accelerating in the first half of the stroke, and a slightly smaller opening during the second half of the stroke.

For the opposite side, the crank on lever 39, crank 52, link 53, supplementary crank 51, link 49 and compensating lever 45 similarly influence the motion of speed control valve 34.

The proposed duplex double acting plunger or piston type general service pump is driven by a pair of clean oil hydraulic cylinders with oil control valve and valve gear designed to obtain the ideal piston velocity and displacement pattern described by as shown in FIGURE 5 and FIGURE 6. In this cycle one piston necessarily lags 90 or A cycle behind the other.

FIGURE 3 shows a form of reversing valve 59 which generally functions in similar fashion to the reversing valve 28 shown in FIGURE 2. Ports 57 and 58 are provided in the ends 60 and 61 to provide means for exhausting fluid into chambers 62 and 63 rather than providing for direct exhaust into these chambers.

FIGURE 3 shows the reversing valve 28 which cuts off both supply and exhaust at mid position and alternately connects each end of the power cylinder to supply or exhaust in operation. The speed control valve shown in FIG- URE 4 includes contours 55 shaped to control the piston speed and cut-off the oil supply at the end of the stroke. The :bridge 56 in the center of the valve does not throttle the outlet to the reversing valve, but seals off the unused supply port when the contoured speed control is throttling the other supply port.

Venting conduits and 70 provide means for draining away leakage past valves 34 and 34. The conduits 70 and 70 connect both of the outer ends of the valves 34 and 34' to exhaust pressure.

Although the invention has been described with reference to specific apparatus it will be appreciated that a wide variety of changes may be made within the ability of one skilled in the art without departing from the scope of this invention. For example, some of the components of the apparatus may be reversed, certain features of the invention may be used independently of others and equivalents may be substituted for the apparatus, all within the spirit and scope of the invention as defined in the appended claims.

What is claimed is:

1. A positive displacement pump of the reciprocating type comprising a pair of pumping cylinders each including reciprocating plunger-like means, power means connected to each of the plunger means, supply means selectively associated with each of the power means to supply power fluid to said power means at a fixed or variable capacity, as desired, to cause said power means to drive said plunger like means to provide a desired pump output, first and second conduit means connecting said supply means to each of said power means, a first and second valve disposed in said first conduit, a first and second valve disposed in said second conduit, all of said valves operative to selectively control passage of power fluid through said first and second conduit means to said power means and to selectively control return of said power fluid to said supply means, movable rod means connecting said first valve of said first conduit means to one of said plunger-like means, movable rod means connecting said first valve of said second conduit means to said other plunger-like means, means movably connecting said secnd valve of said first conduit means to said other plungerlike means so that said other plunger-like means controls primary movement of said second valve of said first conduit means, means movably connecting said second valve of said second conduit means to said one plungerlike means so that said one plunger-like means controls primary movement of said second valve of said second conduit means, and means movably interconnecting each of said last mentioned means whereby secondary movement of said second valve of said first conduit means is controlled by said one plunger-like means and secondary movement of said second valve of said second conduit means is controlled by said other plunger-like means.

2. The positive displacement pump claimed in claim 1 wherein a second pair of plunger-like means is connected to each of the power means and each of said plunger-like means is disposed opposite to and in alignment with a plunger-like means of said first pair of plunger-like means.

3. A positive displacement pump of the reciprocating type including means which facilitates obtaining a constant and non-pulsating rate of flow of fluid into and out of the pump and optimum piston velocity throughout the working cycle or stroke of the pump, said positive displacement pump comprising a pair of pumping cylinders each including reciprocating plunger-like means, power means connected to each of the plunger means, supply means selectively associated with each of the power means to supply power fluid to said power means at a fixed or variable capacity, as desired, to cause said power means to drive said plunger-like means to provide a desired pump output, first and second conduit means connecting said supply means each of said power means, a first and second valve disposed in said first conduit a first and second valve disposed in said second conduit, all of said valves operative to selectively control including reciprocating plunger-like means, power cylinders connected to each of the plunger-like means, supply means selectively associated with each of the power cylinders to supply power fluid to said power cylinders at a fixed or variable capacity, as desired, to cause said power cylinders to drive said plunger-like means to provide a desired pump output, first and second conduits connecting said supply means to each of said power cylinders, a reversing valve and a speed control valve in said first conduit, a reversing valve and a speed control valve in said second conduit, all of said valves operative to selectively control passage of power fluid to said power cylinders and to selectively control return of said power fluid to said supply means, rod means movably connecting said reversing valve of said first conduit to one of said plunger-like means, rod means movably connecting said speed control valve of said first conduit to said other plunger-like means, so that said other plunger-like means controls primary movement of said speed control valve of said first conduit, rod means movably connecting said reversing valve of said second conduit to said other plunger-like means, rod means movably connecting said speed control valve of said second conduit to said one plunger-like means so that said one plunger-like means controls primary movement of said speed control valve of said second conduit, and means movably interconnecting each of said rod means for the speed control valves whereby passage of power fluid through said first and second conduit means to said power means and to selectively control return of said power fluid to said supply means, movable rod means connecting said first valve of said first conduit means to one of said plunger-like means, movable rod means connecting said first valve of said second conduit means to said other plunger-like means, means movably connecting said second valve of said first conduit means to said other plungerlike means so that said other plunger-like means controls primary movement of said second valve of said first conduit means, means movably connecting said second valve of said second conduit means to said one plungerlike means so that said one plunger-like means controls primary movement of said second valve of said second conduit means, and a lever and crank arrangement interconnecting each of said last mentioned means whereby secondary movement of said second valve of said first conduit means is controlled by said one plunger-like means and secondary movement of said second valve of said second conduit means is controlled by said other plungerlike means.

4. A positive displacement pump of the reciprocating type including means which facilitates obtaining a constant and non-pulsating rate of flow of fluid into and out of the pump and optimum piston velocity throughout the working cycle or stroke of the pump, said positive displacement pump comprising a pair of pumping cylinders each including reciprocating plunger-like means, power cylinders connected to each of the plunger-like means, supply means selectively associated with each of the power cylinders to supply power fluid to said power cylinders at a fixed or variable capacity, as desired, to cause said power cylinders to drive said plunger-like means to provide a desired pump output, first and second conduits connecting said supply means to each of said power cylinders, a reversing valve and a speed control valve in said first conduit, a reversing valve and a speed control valve in said second conduit, all of said valves operative to selectively control passage of power fluid to said power cylinders and to selectively control return of said power fluid to said supply means, rod means movably connecting said reversing valve of said first conduit to one of said plunger-like means, rod means movably connecting said speed control valve of said first conduit to said other plunger-like means, so that said other plunger-like means controls primary movement of said speed control valve of said first conduit, rod means movably connecting said reversing valve of said second conduit to said other plunger-like means, rod means movably connecting said speed control valve of said second conduit to said one plunger-like means so that said one plunger-like means controls primary movement of said speed control valve of said second conduit, and means movably interconnecting each of said rod means for the speed control valves whereby secondary movement of said speed control valve "of said first conduit is controlled by said one plunger-like means and secondary movement of said speed control valve of said second conduit is controlled by said other plunger-like means.

5. A positive displacement pump of the reciprocating type including means which facilitates obtaining a constant and non-pulsating rate of flow of fluid into and out of the pump and optimum piston velocity throughout the work ing cycle or stroke of the pump, said positive displacement pump comprising a left hand and a right hand pumping cylinder each including reciprocating plunger-like means, power cylinders to supply power fluid to said power cylinders at a fixed or variable capacity, as desired, to cause said power cylinders to drive said plunger-like means to provide a desired pump output, first and second conduits connecting said supply means to each of said power cylinders, a reversing valve and a speed control valve in said first conduit, a reversing valve and a speed control valve in said second conduit, all of said valves operative to selectively control passage of power fluid to said power cylinders and to selectively control return of said power fluid to said supply means, rod means movably connecting said reversing valve of said first conduit to said right hand plunger-like means, rod means movably connecting said speed control valve of said first conduit to said left hand plunger-like means, so that said left hand plunger-like means controls primary movement of said speed control valve of said first conduit, rod means movably connecting said reversing valve of said second conduit to said left hand plunger-like means, rod means movably connecting said speed control valve of said second conduit to said right hand plunger-like means so that said right hand plunger-like means controls primary movement of said speed control valve of said second conduit, and a mechanical arranagement including a lever and crank movably interconnecting each of said rod means for the speed control valves whereby secondary movement of said speed control valve of said first conduit is controlled by said right hand plunger-like means and secondary movement of said speed control valve of said second conduit is controlled by said left hand plunger-like means.

6. The positive displacement pump claimed in claim 5 wherein a second pair of plunger-like means is connected to each of the power means and each of said plunger-like means is disposed opposite to and in alignment with a plunger-like means of said first pair of plunger-like means.

7. A valve arrangement adapted for use with a positive displacement pump of the reciprocating type including means which facilitates obtaining a constant and nonpulsating rate of flow of fluid into and out of the pump and optimum piston velocity throughout the working cycle or stroke of the pump, said positive displacement pump comprising a left hand and right hand pumping cylinder each including reciprocating plunger-like means, power means connected to each of the plunger-like means, supply power fluid to said power means at the fixed or variable capacity, as desired, to cause said power means to drive said plunger-like means to provide a desired pump output, first and second conduit means connecting said supply means to each of said power means, said valve arrangement comprising first and second conduit means connecting said supply means to each of said power means, a first and second valve disposed in said first conduit a first and second valve disposed in said second conduit, all of said valves operative to selectively control passage of power fluid through said first and second conduit means to said power means and to selectively control return of said power fluid to said supply means, movable rod means connecting said first valve of said first conduit means to said right hand plunger-like means, movable rod means connecting said first valve of said second conduit means to said left hand plunger-like means, means movably connecting said second valve of said first conduit means to said left hand plunger-like means so that said left hand plunger-like means controls primary movement of said second valve of said first conduit means, means movably as connecting said second valve of said second conduit means to said right hand plunger-like means so that said right hand plunger-like means controls primary movement of said second valve of said second conduits means, and means movably interconnecting each of said last mentioned means whereby secondary movement of said second valve of said first conduit means is controlled by said right hand plunger-like means and secondary movement of said second valve of said second conduit means is controlled by said left hand plunger-like means.

8. A valve arrangement adapted for use with a positive displacement pump of the reciprocating type including means which facilitates obtaining a constant and nonpulsating rate of flow of fluid into and out of the pump and optimum piston velocity throughout the working cycle or stroke of the pump, said positive displacement pump comprising of a left hand and right hand pumping cylinder each including reciprocating plunger-like means, power cylinders connected to each of the plunger-like means, supply means selectively associated with each of the power cylinders to supply power fluid to said power cylinders at a fixed or variable capacity, as desired, to cause said power cylinders to drive said plunger-like means to provide a desired pump output, first and second conduits connecting said supply means to each of said power cylinders, said valve arrangement comprising a reversing valve and a speed control valve in said first conduit, a reversing valve and a speed control valve in said second conduit, all of said valves operative to selectively control passage of power fluid to said power cylinders and to selectively control return of said power fluid to said supply means, rod means movably connecting said reversing valve of said first conduit to said right hand plunger-like means, rod means movably connecting said speed control valve of said first conduit to said left hand plunger-like means, so that said left hand plunger-like means controls primary movement of said speed control valve of said first conduit, rod means movably connecting said reversing valve of said second conduit to said left hand plunger-like means, rod means movably connecting said speed control valve of said second conduit to said right hand plunger-like means so that right hand plunger-like means controls primary movement of said speed control valve of said second conduit, and means movably interconnecting each of said rod means for the speed control valves whereby secondary movement of said speed control valve of said first conduit is controlled by said right hand plunger-like means and secondary movement of said speed control valve of said second conduit is controlled by said left hand plunger-like means.

References Cited UNITED STATES PATENTS 2,141,731 12/1938 'Wolfrom et al 10349 3,179,056 4/1965 Wright 10349 ROBERT M. WALKER, Primary Examiner. 

1. A POSITIVE DISPLACEMENT PUMP OF THE RECIPROCATING TYPE COMPRISING A PAIR OF PUMPING CYLINDERS EACH INCLUDING RECIPROCATING PLUNGER-LIKE MEANS, POWER MEANS CONNECTED TO EACH OF THE PLUNGER MEANS, SUPPLY MEANS SELECTIVELY ASSOCIATED WITH EACH OF THE POWER MEANS TO SUPPLY POWER FLUID TO SAID POWER MEANS AT A FIXED OR VARIABLE CAPACITY, AS DESIRED, TO CAUSE SAID POWER MEANS TO DRIVE SAID PLUNGER THE MEANS TO PROVIDE A DESIRED PUMP OUTPUT, FIRST AND SECOND CONDUIT MEANS CONNECTING SAID SUPPLY MEANS TO EACH OF SAID POWER MEANS, A FIRST AND SECOND VALVE DISPOSED IN SAID FIRST CONDUIT, A FIRST AND SECOND VALVE DISPOSED IN SAID SECOND CONDUIT, ALL OF SAID VALVES OPERATIVE TO SELECTIVELY CONTROL PASSAGE OF POWER FLUID THROUGH SAID FIRST AND SECOND CONDUIT MEANS TO SAID POWER MEANS AND TO SELECTIVELY CONTROL RETURN OF SAID POWER FLUID TO SAID SUPPLY MEANS, MOVABLE ROD MEANS CONNECTING SAID FIRST VALVE OF SAID FIRST CONDUIT MEANS TO ONE OF SAID PLUNGER-LIKE MEANS, MOVABLE ROD MEANS CONNECTING SAID FIRST VALVE OF SAID SECOND CONDUIT MEANS TO SAID OTHER PLUNGER-LIKE MEANS, MEANS MOVABLY CONNECTING SAID SECOND VALVE OF SAID FIRST CONDUIT MEANS TO SAID PLUNGERLIKE MEANS SO THAT SAID OTHER PLUNGER-LIKE MEANS CONTROLS PRIMARY MOVEMENT OF SAID SECOND VALVE OF SAID FIRST CONDUIT MEANS, MEANS MOVABLY CONNECTING SAID SECOND VALVE OF SAID SECOND CONDUIT MEANS TO SAID ONE PLUNGERLIKE MEANS SO THAT SAID ONE PLUNGER-LIKE MEANS CONTROLS PRIMARY MOVEMENT OF SAID SECOND VALVE OF SAID SECOND CONDUIT MEANS, AND MEANS MOVABLY INTERCONNECTING EACH OF SAID LAST MENTIONED MEANS WHEREBY SECONDARY MOVEMENT OF SAID SECOND VALVE OF SAID FIRST CONDUIT MEANS IS CONTROLLED BY SAID ONE PLUNGER-LIKE MEANS AND SECONDARY MOVEMENT OF SAID SECOND VALVE OF SAID SECOND CONDUIT MEANS IS CONTROLLED BY SAID OTHER PLUNGER-LIKE MEANS. 